Fluid pressure motor



July 13, 1965 J. H. FEASTER FLUID PRESSURE MOTOR 2 Sheets-Sheet 1 Filed May 25. 1962 IN V EN TOR. era/0v F, EASTER Arraew July 13, 1965' J. H. FEASTER FLUID. PRESSURE MOTOR 2 Shee ts-Sheet 2 Filed May 25, 1962 INVENTOR. 750 17. EASTER 384 y 98 W 4* 4rrae/vsY United States Patent 3,194,123 FLUID PRESSURE MUTUR John H. Fcaster, 703 Eastwood Ave, Santa Ana, Filed May 25, 1962, Ser. No. 197,721

8 Claims. (Cl. 91-176) The present invention relates generally to fluid pressure motors, and more particularly to such motors which employ radially disposed pressure responsive actuators.

Heretoforc, motors have usually been so constructed as to comprise a crankshaft operatively connected to a drive shaft. The crankshaft in such prior devices is usually formed with a crank throw for each piston employed in the engine. Such crank throws are generally spaced along the crankshaft so that each cylinder is substantially separate and independent from all other cylinders.

In view of the foregoing, prior motors have required separate valve means for each cylinder. As a result, such prior art devices have been relatively large and cumbersome.

It has long been the desire in the manufacture of motor vehicles, such as automobiles, tractors and the like, to provide a motor which is relatively small and compact for direct attachment to a wheel or other member to be rotatively driven. Such motive power means should be relatively simple in construction and hence less expensive to manufacture and maintain than present day conventional motors. Also, the compactness wouldrin any circumstances, result in a considerable saving of valuable space.

It is an object of the present invention to provide motive power means which is simple in construction and which operates from a relatively fixed source of fluid pressure.

Another object of the present invention is to teach the construction of a fluid pressure motor, wherein a portion of the power generated thereby is employed to operate the necessary valve means for controlling the operation of the motor.

Another object of the present invention is to provide a fluid pressure motor as characterized above which employs a plurality of radially disposed fluid pressure actuators.

Another object of the present invention is to provide a fluid pressure motor as characterized above wherein the fluid pressure actuators are sequentially operated to provide a sustained driving force on the drive member associated therewith.

Another object of the present invention is to provide a fluid pressure motor as characterized above wherein the fluid pressure actuators are rectilinearly operable.

A further object of the present invention is to provide a fluid operated motor as characterized above which can be attached to or mounted within the member to be rotatably driven.

A still further object of the present invention is to teach the construction of a fluid pressure motor as characterized above which is simple and inexpensive to manufacture and which is rugged and dependable in operation.

The novel features which I consider characteristic of my invention are set forth with particularity in the appended claims. The device itself, however, both as to its organization and mode of operation, together with additional objects and advantages thereof, will best be understood from the following description of a specific 'ice FIGURE 2 is a fragmentary side elevational view of the driven member of FIGURE 1;

FlGURE 3 is a fragmentary sectional view taken substantially along line lie-3 of FIGURE 2;

FIGURE 4 is a fragmentary sectional view taken substantially along line 4-4 of FIGURE 3;

FIGURE 5 is a fragmentary sectional view taken substantially along line 5-5 of FIGURE 4;

FIGURE 6 is a fragmentary exploded perspective view of mounting means for the end of one of the fluid pressure actuators; and

FIGURE 7 is a fragmentary sectional view taken substantially along line 7-7 of FIGURE 2.

Like reference characters indicate corresponding parts throughout the several views of the drawings.

Referring to FIGURE 1 of the drawings, there is shown therein, a preferred embodiment for illustration of the present invention. Generally, such embodiment comprises a driven member 10 and a source of fluid pressure therefor, designated generally by the arrow 12.

The source of fluid pressure 12 may take substantially any desired form and is shown in FIGURE 1 as comprising a pump 14 and a four-way valve 16 formed with flow control ports 16a, 16b, 16c and 16d. Interconnecting the pump 14 and valve 16, as schematically shown in FIG- URE 1, are suitable fluid conduits. A conduit 18 connects the outlet of the pump 14 to the port 16d of valve 16. A conduit 20 connects a supply or sump tank 21 to the port ltib of valve 16 and to the inlet of the pump 14. As will be hereafter described in further detail, a fluid conduit 22 connects port 16c of the valve 16 to the inlet to the member 10 and a conduit 24 interconnects the outlet of member it) to the port 16a of switch 16. A rotatable flow control member 16a is provided for control of ports Ma, 1612, 16c and 16d.

Referring now to FIGURE 3 of the drawings, there is provided therein a flanged journal member 26 having a tubular journal portion 26a and suitable flange means 261;. The flanges 2511 may be provided with suitable mounting holes 26c whereby, through the use of suitable mounting bolts, journal member 26 can be rigidly secured to a base member or to a vehicular device to be propelled.

Within the journal portion 26a of member 26 there is positioned a stationary crankshaft 28 having a journal member 3t) and a crank throw member 34, fluid pressure distributor 38 and a cylindrical mounting member 40.

Crankshaft 23 is formed as a unitary structure, the axis of the cylindrical distributor 38 being offset from the axis of mounting member 4% and journal member 30 as afforded by crank throw member 34.

Removably fastened to distributor 38 is a unitary structure comprising a crank throw member 36 and a journal member 32. Suitable fastening means such as bolt 37 which extends through a suitably counter-sunk opening in member 36 and threadedly engages an extension on the side of distributor 38 positions journal member 32 so that its axis is aligned with the axis of the journal member 3t) of crankshaft 28. Such extension may be employed to insure proper alignment of the journal members 3d and 32.

Formed intermediate the journal member 30 and the mounting portion 40 of crankshaft 28 is a plurality of circumferentially spaced radially extending bevelled splines 4-2, each of which slidably fits within a suitably formed cut-out or notch in the end of journal portion 26a of member 26. The crankshaft 28 is: assembled to member 26 by mounting portion 40 thereof being inserted into journal portion 26a as shown in FIGURE 3, the bevelled splines 42 being inserted into the respective notches therefor. A washer 44 is then fitted over the threaded section 46a of mounting portion 4% and a lock nut 46 is threadedly fastened on the portion 4% to firmly secure the splines 42 in their assembled positions.

Formed in crankshaft 28 are inlet and outlet passageways 50 and 52 respectively which conduct fluid under pressure as will hereinafter appear.

The end 40a is reduced at section 4012 which receives slip ring 53 journalcd thereon. This slip ring 53 is held against axial movement by means of a washer 54 and nut 55. In the embodiment shown the fluid from conduit 22 may flow through port as and annular groove 57 and passage 58 to the passage Stl. Similarly, passage 52 communicates with conduit 24 through passage 59, annular groove 6t) and port 61. If desired appropriate O-ring seals are located on either side and between the annular grooves 57 and es.

Suitable bearing means as shown at 64 and 66 are fitted onto the journal portions 26a and 39 respectively. It is desirable that the outer cylindrical bearing surface of journal portion M) be substantially the same size and shape as the bearing surface of journal portion 26a so that the bearing members 64 and 66 can be substantially identical.

Positioned on the outer races of the bearing members 64 and 66 is one side of the member to be driven by the subject motor. Such member may take substantially any desired form and, in the event it is to be used for driving a vehicle, it may take the form of a drive Wheel. However, the particular shape and design of the drive member has no influence on the scope of the present invention. It is shown in the drawings as substantially square and as comprising a pair of side plates 72 and 74 which are joined together by a four sided box structure '76 comprised of side members 75a, 76b, 76c and 76d.

Each of the side plates 72 and '74 is provided with its own hub as shown at 72a and 74a respectively. The hub 72a. is provided with a large central opening for receiving the bearing members 64 and 66 whereby the side plate '72 is permitted to freely rotate about journal portions 26a and 30.

The hub 74a and side plate 74 is rotatably mounted on the journal portion 32 by bearing means 76 as shown in FIGURE 3. If desired, the outer races of the bearing members 64 and '76 may be held in assembled position Within the respective hubs 72a and 74a by means of snap ring retainers as shown at 78 and 86).

As shown more particularly in FIGURE 3, the inlet and outlet passageways d and 52 formed in crankshaft 23 extend through mounting portion 443, journal portion 3t) and crank throw 28 into the axially oflfset distributor member 38. As shown in FIGURES 3 and 4, distributor member 38 is formed substantially symmetrically with a pair of oppositely disposed substantially large grooves 38a and 38b. On either side of each of the grooves 38a and 38b is a smaller groove. Disposed on opposite sides of groove 33a are grooves 33c and 38d, and on opposite sides of groove 38!), are grooves 38c and 38f.

As shown most clearly in FIGURE 5 of the drawings, distributor member 33 is further formed with a relatively large passageway 33g which interconnects the inlet passageway 5d of crankshaft 28 with the relatively large groove 38a in the cylindrical periphery of distributor 38. In like fashion, there are smaller passageways 3H1 and 355i which effect communication between inlet passageway 56 and the smaller grooves 38@ and 33 respectively on the side of distributor 33 opposite the groove 38a.

There is also formed in distributor 38 a large passageway 38]: which interconnects outlet or exhaust passageway 52 and groove 33!], and a pair of smaller passageways 38! and 33m which interconnect such outlet passageway 52 with the smaller grooves 330 and 38d respectively.

Rotatably mounted on the cylindrical distributor 38 is a valve member 84 which is tubular in construction and .is formed with four circumferentially spaced radially extending openings or ports 84a, 84b, 84c and 84d, as most clearly shown in FIGURE 4.

Positioned about the valve member 84 are the inner end portions of a plurality of radially disposed fluid pressure actuators. Such actuators are shown most clearly in FIGURE 2 at as, $8, 90 and 92, and may take substantially any desired form. The actuators of the present embodiment are rectilinearly operable in response to the application of fluid pressure as will hereinafter become more apparent. Each of such devices shown in the drawings comprises a pair of relatively movable members which may take the form of a cylinder as shown at 88a in FLGURE 2 which carries a piston 83b, the piston, of course, being movable with respect to the cylindcr in response to the application of fluid pressure. The pressure responsive devices 86, 88, 90 and 92 shown in the drawings are radially disposed such that the pistons are disposed outwardly while the cylinders therefor are positioned radially inwardly.

As shown most clearly in FIGURE 4, the inner end portion of each of the cylinders of the pressure responsive actuators, is flared or flanged as shown at 86c, 88c, Qtlc and @2c. Such flared end portions are formed to sealingly engage the cylindrical outer surface of valve member 84- so as to provide a hermetic seal therebetween for purposes which will be hereinafter described. Each of said cylinder members is, of course, formed with a central opening through which the fluid pressureway pass. Additionally, in order to assist in effecting the afore mentioned hermetic seal, each of the cylinder members is formed with an annular feathered lip within the respective central opening thereof adjacent the valve member 84 as shown at 85d, 88d, 90d and 2d. Such feathered or tapered lips are urged by the fluid pressure into sealing engagement with the valve member 84 to assist in sealing the space therebetween.

The flanged end portions of the cylinders of the fiuid pressure actuators are held in assembled relation with valve member 84 by a pair of mounting rings 94 and as as shown most clearly in FIGURE 3.

Positioned between each pair of adjacent end portions of the fluid pressure actuators on member 84 is limit stop means in the form of pins; as shown at 98, 100, 192 and 1M, inserted into suitably formed openings in valve member 84. In order to equalize the stopping effect on the respective actuators, a pair of such pins is provided between each pair of adjacent end portions of the pressure responsive actuators as shown most clearly in FIG- URE 5.

Each of the piston members of the pressure responsive actuators is formed with an enlarged V-shaped end portion, as shown most clearly in FIGURE 6 wherein the actuator 3% is provided with an end portion 88g for the radially outward end portion of its piston member 8821. The pointed end of each of the V-shaped end portions is positioned against an L-shaped pressure plate as shown most clearly at 11 in FIGURE 6. Each such pressure plate is held in assembled position within a corner of the substantially square box frame 76 by any suitable means.

Attached to the inner surface of each of the side plate 72 and 74 of the driven member ltl is an arcuate retainer as shown at 112 and 114-. As will be readily understood by those persons skilled in the art, there is provided in the embodiment shown in the drawings, a pair of such arcuate retainers for each of the outwardly extending end portions of the pressure responsive actuators.

As shown most clearly in FIGURE 7, positioned between the V-shaped enlarged end portion of each of the actuators and the respective arcuate retainers are brass wear plates as shown in 116 and 113. Suitable compression spring means may be provided between the enlarged end portions and the respective wear plates to urge such wear plates into firm sliding engagement with the respective arcuate retainers. FIGURE 7 shows a pair of compression springs 12% and 122 suitably posi tioned in recesses formed in the enlarged end portion 88g for urging respectively the Wear member 116 into engagement with retainer 112, and the wear member 118 into engagement with the retainer 114. In the interest of providing smooth sliding engagement between the wear members and the arcuate retainers, it is preferable that the Wear members be formed of brass.

As shown most clearly in FIGURE 5 of the drawings, it may be desirable to provide distributor 38 with suitable openings as at 124 and 126 for connecting several of the subject fluid pressure motors in tandem. In such event, it may be desirable to have all of the motors receive fluid pressure from passageway 5t and to have all of them exhaust into return passageway 52. Thus with the passageways 124 and 126 as shown in FIGURE 5, it is possible to add any desired number of fluid pressure motors, the fluid pressure circuits therefor being arranged in parallel.

During use there will be leakage of fluid out of the area of distributor 38 into'the casing formed by side plates 72 and 74 with box structure '76. Accordingly a vent or leakage return passage 128 in the mounting portion 40 communicates the interior of the casing with a return line 130 which leads back to the sump tank 21. The return line 130 is connected to the portion 40 by means of a rotatable fitting 131 which permits the crank shaft 28 to rotate relative to the return line.

The subject apparatus operates generally as follows:

The embodiment shown in the drawings is so operable as to be rotatable in the direction indicated by the arrows 130 shown in FIGURES 2 and 4. The first step in effecting rotation of the member 10, is to actuate the valve 16 of FIGURE 1 to its open position as shown. Thus, with the rotatable valve member 16e positioned as shown, fluid pressure is permitted to flow from pump 14 through conduit 18, port 16d, port 16c and conduit 22 to the subject motor. In like fashion, the fluid is permitted to return to sump tank 21 and pump 14 from the subject motor through conduit 24, port 16a, port 16b and conduit 20.

The fluid under pressure from pump 14 flows from conduit 22 through fluid inlet passageway 50 within crankshaft 28 to distributor 38. It then flows through opening 38g into the large arcuate groove 38a in me1nber 38. With the motor in the position shown in FIG- URE 4, such inlet fluid pressure is admitted only to pressure responsive actuator 92 through port 84d of valve member 84. This applies pressure to the piston member of actuator 92 so as to cause the latter to exert a force on the respective corner of the driven member it). Since the radially inward end of actuator 92 is, at this time, offset from the axis of rotation of the driven member 10, such force applied by actuator 92 is divided into a pair of components, one of which is at right angles to the radius of the driven member to effect rotation thereof about the axle portions 30 and 32 of the crankshaft 28.

The actuators 86 and 90, at this time, are inactive since the ports 84c, and 84a of valve member 84 are closed at this time.

The pressure responsive actuator 88, on the other hand, is being exhausted while actuator 92 is being actuated to move the driven member 10 in a forward direction. This results by virtue of the fact that port 8451 of valve member 84 is, at this time, aligned with the groove actuator to the groove 38a of distributor 38, such actuator commences to operate to apply a driving force to the the valve 84. That is, with pressure being applied to such valve member through opening 38g and groove 38a, a counter balancing force is applied to the opposite side of member 84 through the openings 3311 and 38 and the small-er arcuate, grooves 38a and 38f formed in distributor 38. In like fashion, the forces acting on valve member 84 due to exhausting of fluid pressure through opening 38k and groove 38b are balanced by the forces acting through opening 381 and 38m, and grooves 38c and 33d. To further balance the forces acting on valve member 84 so as to insure sealing engagement thereof with adjacent members, I prefer to form the inner surface of member 84 with enlarged slots or cut-outs as shown at 34a and 84f. Such cut-outs tend to further equalize the pressure from the large openings 33b and 33g of distributor 38.

As will be readily apparent to those persons skilled in the art, that with distributor 33 offset or displaced from the axis of rotation of driven member 16, the flanged inner end portions of the actuators must be permitted to move on valve member 84 as such actuators are moved between their power of actuating positions and their exhaust positions. To limit such movements, the limit stops 98, 1053, 102, and 104 are provided.

It is thus seen that the present invention provides a small compact fluid pressure motor which can be used for effecting rotation of substantially any driven member. Such rotation of course, takes place on the bearing members 64, 66 and 76, about the central axis of the axle members 3t and 32. When it is desired to interrupt the operation of the subject motor, it is merely necessary to rotate valve member 16a such as to interrupt the control ports of valve 16.

It is thus seen that the present invention teaches the construction of a fluid pressure motor having a plurality of radially disposed pressure responsive actuators.

The preferred embodiment disclosed is primarily intended fora use to drive the driven member 10 with the crankshaft 28 remaining stationary. It should be noted, however, that because of the use of rotatable fitting 131, the slip ring 53 and the annular grooves 57 and iii), the crankshaft 28 may be rotated relative to the conduits 13d, 22 and 24. Therefore, the crankshaft 28, with the components attached to flanged member 26 can be rotated with the driven member 10 held stationary.

Although I have shown and described certain specific embodiments of my invention, I am fully aware that many modifications thereof are possible. My invention, therefore, is not to be restricted except insofar as is necessitated by the prior art and by the spirit of the appended claims.

1. A fluid pressure motor comprising in combination, a drive member mounted for rotation about a given axis, a plurality of generally radially disposed fluid pressure responsive actuators each of which comprises a pair of relatively rectilinear-1y movable actuator members one of which is pivotably connected to said drive member, a source of fluid pressure for said actuators comprising a relatively tion of said valve member on said distributor member being oflset from the axis of rotation of said drive member whereby relative rectilinearly movement of said actuator members develops a component force urging said drive member in a given direction of rotation, said last mentioned means permitting each said other actuator member to have a predetermined limited range of movement relative to said valve member, said movement being suflicient to accommodate the swinging of each said other actuator member relative to the valve member resulting during rotation of the drive member because of the olfset of the axis of the valve member from the given axis.

2. A fluid pressure motor according to claim 1, wherein the rectilinearly movable actuator members comprise a cylinder, one end of which is connected to said valve member for a limited range of movement and a piston cooperable with said cylinder one end of which is pivotally connected to said drive member.

3. A fluid pressure motor according to claim Tl, wherein the means for pivotally connecting said one of said actuator members to said drive member comprises an angle member fastened to said drive member, a pivot member fixed to said one of said actuator members and formed with a tapered portion for insertion in said angle member, and means for retaining said tapered portion in said angle member.

4. A fluid pressure motor according to claim 3 wherein said retaining means comprises a member formed with an arcuate surface, and biasing means operatively interposed between said pivot member and said arcuate surface whereby the tapered portion of said pivot member is retained in said angle member throughout pivotal movement of the respective actuator.

5. A fluid motor comprising: a frame; a crankshaft mounted on said frame for rotation about a first axis, said crankshaft having an offset portion;

a plurality of generally radially disposed fluid pressure actuators drivingly connected to said offset portion and said frame, each of said actuators having two ends, one end of each actuator connected to said offset portion;

means for supplying fluid at a working tially to said fluid pressure actuators; means connecting the other end of each actuator to said frame, said last mentioned means comprising;

a pressure plate secured to said frame, said pres sure plate having a notch facing said offset portion;

an enlarged V-shaped portion on the other end of the actuator, said V-shaped portion having a bearing edge at the point or" the V, the point of the V-shape being received in said notch;

an arcuate retainer secured to said frame and slidably engaging said enlarged V-shaped portion, said arcuate retainer projecting at least partially between said enlarged V-shaped portion and said offset portion so as to prevent the said other end of the fluid actuator from moving away from the pressure plate, whereby the fluid actuator may swing relatively to the frame to accommodate the motion of the offset portion as the crankshaft rotates relative to said frame.

6. The fluid motor set forth in claim 5 including spring loaded bearing means between said V-shaped portion and said arcuate retainer.

DIT'ZSSUIE sequen- 7. A fluid motor comprisin":

a frame;

a crankshaft mounted on said frame forrotation about a first axis, said crankshaft having an offset portion;

a plurality of fluid actuators disposed in a plane at a right angle to said axis and extending generally radially from said offset portion, said actuators each having two ends, one end of each actuator connected to said frame;

means for supplying working fluid through the interior of said offset portion and sequentially supplying said fluid to said actuators to effect rotation of the shaft relative to the frame, said means including:

a valve member rotatably mounted on said offset portion, the other end of each fluid actuator engaging the valve member at different positions thereon;

means communicating the interior of each actuator with the offset portion, said means including a separate opening through said valve member at the position of each actuator, each said opening being larger on the inward side of the valve member than the outward side, whereby fluid pressure in each said port tends to force the valve member away from the offset portion at that point.

3. A fluid motor comprising:

a frame;

a crankshaft mounted on said frame for rotation about a first axis, said crankshaft having an offset portion;

a plurality of generally radially extending fluid actuators, each actuator having two ends and a working chamber formed by a piston and a cylinder of predetermined cross-sectional area, each of said actuators having one end connected to said frame;

means for sequentially supplying fluid pressure to said actuators from the interior of said offset portion through the other end of each respective actuator, said means including a valve member rotatably mounted on said offset portion, the other end of each actuator engaging said valve member, a separate port in said valve member opening into the other end of each respective actuator through a port in each other end, the cross-sectional area of each said last mentioned port being smaller than said predetermined area, whereby pressure in the working chamber forces the other end of the actuator against the valve member to at least partially seal the actautor with the valve member.

References Cited by the Examiner UNlTED STATES PATENTS FRED E. ENGELTHALER, Primary Examiner.

RICHARD B. WILKINSON, Examiner. 

1. A FLUID PRESSURE COMPRISING IN COMBINATION, A DRIVE MEMBER MOUNTED FOR ROTATION ABOUT A GIVEN AXIS, A PLURALITY OF GENERALLY RADIALLY DISPOSED FLUID PRESSURE RESPONSIVE ACTUATORS EACH OF WHICH COMPRISES A PAIR OF RELATIVELY RECILINEARLY MOVABLE ACTUATOR MEMBERS ONE OF WHICH IS PIVOTABLY CONNECTED TO SAID DRIVE MEMBER, A SOURCE OF FLUID PRESSURE FOR SAID ACTUATORS COMPRISING A RELATIVELY STATIONARY DISTRIBUTOR MEMBER HAVING INLET AND OUTLET FLUID PASSAGEWAYS AND A VALVE MEMBER ROTATABLY MOUNTED ON SAID DISTRIBUTOR MEMBER AND FORMED WITH VALVE PORTS FOR COOPERATION WITH THE PASSAGEWAYS IN SAID DISTRIBUTOR MEM BER, AND MEANS CONNECTING THE OTHER ACTUATOR MEMBER OF EACH OF SAID PAIRS TO SAID VALVE MEMBER, THE AXIS OF ROTATION OF SAID VALVE MEMBER ON SAID DISTRIBUTOR MEMBER BEING OFFSET FROM THE AXIS OF ROTATION OF SAID DRIVE MEMBER WHEREBY RELATIVE RECTILINEARLY MOVEMENT OF SAID ACTUATOR MEMBERS DEVELPS A COMPONENT FORCE URGING SAID DRIVE MEMBER IN A GIVEN DIRECTION OF ROTATION, SAID LAST MENTIONED MEANS PERMITTING EACH OF SAID OTHER ACTUATOR MEMBER TO HAVE A PREDETERMINED LIMITED RANGE OF MOVEMENT RELATIVE TO SAID VALVE MEMBER, SAID MOVEMENT BEING SUFFICIENT TO ACCOMMODATE THE SWINGING OF EACH SAID OTHER ACTUATOR MEMBER RELATIVE TO THE VALVE MEMBER RESULTING DURING ROTATION OF THE DRIVE MEMBER BECAUSE OF THE OFFSET OF THE AXIS OF THE VALVE MEMBER FROM THE GIVEN AXIS. 